Frequency compensated oscillator design for process tolerances

ABSTRACT

A continuous or distributed resonator geometry is defined such that the fabrication process used to form a spring mechanism also forms an effective mass of the resonator structure. Proportional design of the spring mechanism and/or mass element geometries in relation to the fabrication process allows for compensation of process-tolerance-induced fabrication variances. As a result, a resonator having increased frequency accuracy is achieved.

BACKGROUND

The present invention relates generally to the design and fabrication ofresonators. Resonators formed in accordance with the present inventionfind application, for example, within oscillators. Within the field ofmicro-electro-mechanical systems (MEMS), oscillators are criticalcomponents. The functionality of many micro-mechanical structures,including oscillators, is based on the reaction (e.g., oscillation,deflection, or torsion) of a spring mechanism to an applied force. Such“spring mechanisms” are typically formed from one or more beamstructures having, or modeled to have, a rectangular cross section ofpredetermined width. The physical structure of a spring mechanism istypically formed using a sequence of planar or surface micro-machiningfabrication processes. The degree to which a spring mechanism actuallytakes the form intended by its design is a function of the precisionwith which the one or more fabrication processes are applied to a layeror segment of a constituent material used to form the spring.

Fabrication processes are applied with well-understood tolerances. Thatis, variations normally occurring in the application of a particularfabrication process result in a micro-mechanical structure havingphysical dimensions that vary from its design specifications. Forrelatively large structures, such small, process-tolerance-inducedvariations are immaterial. However, MEMS components are so small andtheir functionality so demanding that even relatively minor variationsfrom specification will adversely influence performance.

For example, the anisotropy of an etching method used to form a beamstructure will determine the exact width of the beam and any variance ofthat width from design specifications. Line width control duringlithography processes will similarly influence the physical dimensionsof a beam structure.

Process-tolerance-induced variations can result in spring mechanismshaving actual widths that differ greatly from their intended design.Since a spring mechanism's width defines its stiffness, and since theratio of resonator stiffness to resonator mass defines a resonator'sfrequency response to an external stimulus, significant variations inspring width are unacceptable. Currently in the known quartz resonators,such variations are corrected by trimming the mechanical structure tobetter define its frequency in relation to its intended design. However,trimming for silicon based resonators is not a fabrication solutionreadily adapted to the reliable mass manufacture of resonatorcomponents. In order to produce precise resonators using silicon batchprocessing, a better design and/or fabrication solution is required.

SUMMARY OF THE INVENTION

The present invention provides a resonator structure having increasedimmunity to process-tolerance-induced variations in geometry. That is,resonators designed and formed in accordance with the present inventionmay be produced with greater manufacturing yield since the ratio ofeffective spring stiffness to effective mass of the resonator is wellmaintained in relation to the fabrication process forming the resonator.

Thus, in a first aspect, a resonator according to the present inventionprovides a spring mechanism having an actual width defining an effectivemechanical stiffness and a mass element having an effective mass. Theactual width of the spring mechanism is defined by a fabrication processused to form, in one example, a beam structure from a constituentmaterial. Further, the mass element has a geometry defined such thatformation of the actual width by the fabrication process results littlechange to a ratio defined by a change in the effective mechanicalstiffness and a change in the effective mass.

In a second, related aspect, the present invention provides a resonatorcomprising a spring mechanism of predetermined length having an actualwidth defining a mechanical stiffness for the spring mechanism, adefined geometry, and an effective mass. The actual width and theeffective mass of the beam structure are simultaneously defined byapplication of a fabrication process to a constituent material. Thegeometry is defined such that application of the fabrication process tothe constituent material results in little change to a ratio defined bya change in the effective mechanical stiffness and a change in theeffective mass.

The present invention also provides a method of forming a resonator. Inone aspect, the method comprises the steps of defining geometry for aspring mechanism, including an actual width that defines a mechanicalstiffness for the spring mechanism, in relation to a fabrication processused to form the spring mechanism from a constituent material. Themethod further defines geometry for a mass element characterized by aneffective mass in relation to the fabrication process. Upon applicationof the fabrication process to the constituent material little changeresults in a ratio defined by a change in the effective mechanicalstiffness and change in the effective mass.

BRIEF DESCRIPTION OF THE DRAWINGS

In the course of the detailed description to follow, reference will bemade to the attached drawings. These drawings show different aspects ofthe present invention and, where appropriate, reference numeralsillustrating like structures, components, materials and/or elements indifferent figures are labeled similarly. It is understood that variouscombinations of the structures, components, materials and/or elements,other than those specifically shown, are contemplated and are within thescope of the present invention.

FIG. 1A illustrates a conventional, discrete resonator structure;

FIG. 1B illustrates a conventional, continuous resonator structure;

FIG. 1C generally illustrates a process by which a beam width isdefined;

FIG. 2 illustrates an exemplary embodiment of discrete resonatorstructure formed in accordance with the present invention;

FIGS. 3A and 3B are exemplary embodiments of mass element geometriesadapted for use within the context of the present invention;

FIGS. 4A and 4B are exemplary embodiments of continuous resonatorstructures formed in accordance with the present invention; and,

FIG. 4C is an exemplary embodiment of hybrid (discrete/continuous)resonator structure formed in accordance with the present invention.

DETAILED DESCRIPTION

A number of teaching embodiments are presented below which describe tomaking and use of the present invention. The embodiments are selectedexamples. The full scope of the present invention is, however, definedby the claims that follow. Examples of discrete, continuous, and hybridresonators are presented below. Those of ordinary skill in the art willrecognize that the distinction between broad resonator classes is donefor purposes of clarity. The present invention is readily applicable toat least the entire range of resonator structures adapted for use inMEMS.

The term “beam” or “beam/mass structure” is used to broadly denote aclass of mechanical elements commonly used in MEMS to define a frequencyof interest. Beams take many specific forms and may be used, forexample, in the suspension of rigid plates, as lateral oscillators, oras cantilever devices. Beam structures are a natural choice forbearing-less motion detectors. Of particular note, MEMS increasingly usebeams within resonator or oscillator structures, such as clock andsignal filtering circuits. Hereafter, the term “resonator” will be usedto describe any circuit or circuit component comprising an elementdesigned to move, vibrate, react, and/or oscillate to identify, respondto, and/or generate a frequency of interest. The term “resonator”embraces mechanical, electrical, and electromechanical means foraccomplishing the foregoing. The term “spring” or “spring mechanism” isused to broadly connote any element, regardless of geometry, having aneffective mechanical stiffness and susceptible to use within aresonator.

Regardless of variation in specific geometry or intended use, resonatorsmay be conceptually viewed as being continuous, discrete, or hybrid (asbetween continuous and discrete) in nature. For purposes of theexplanation that follows, a discrete oscillator system comprises one ormore independent spring mechanisms having prescribed stiffness(es) andcorresponding mass element(s). The designation “discrete” is used merelyfor clarity of explanation and it is well recognized that no resonatorstructure is completely discrete since the spring mechanism contributesome mass to the oscillation response of the system. In similar vein,every mass element is subject to some bending under the influence of anexternal force. Hence, the term “effective” is used to described anoverall mechanical stiffness for a resonator. The mass element ischaracterized by an effective mass. The term “effective mass” describesthe mass of the mass element as it actually exists within the operative,discrete oscillator, and is often distinct from the design massspecified for the resonator. Within the discrete oscillator system, boththe spring mechanism and mass element are said to have respectivegeometries. The term “geometry” is used to broadly connote the physicaldimensions (e.g., one or more of—height, width, length, radius, angle,circumference, thickness, etc.) and/or the layout design specified for aspring mechanism and/or mass element.

The effective mass of the mass element(s) within the discrete oscillatorsystem, as well as the stiffness of the of the resonator structuresdefine the resonance frequency (f) of the oscillator accordingly to thefollowing relationship: $\begin{matrix}{f = {\frac{1}{2\pi}\sqrt{\frac{\text{stiffness}}{{mass}_{({effective})}}}}} & {{Equation}\quad 1}\end{matrix}$

In contrast to the discrete oscillator, a continuous oscillatorcomprises a spring mechanism without an independent mass element. Incontinuous oscillators formed, as presently preferred, from a beamstructure, the beam structure constitutes both the mass and stiffnesscomponents of the resonator.

FIG. 1A generally shows a discrete oscillator system including a springmechanism 1 fixed at one end to an anchor 3 and at the other end to masselement 2. Spring mechanism 1 and mass 3 are independent one from theother.

FIG. 1B generally shows a continuous oscillator consisting of springmechanism 4 fixed at either end by anchors 3.

In each oscillator type, the spring mechanism possesses a mechanicalstiffness (k_(Y)) in the lateral direction Y that is cubic to its actualwidth (“W_(real)”). The term “actual width” describes the width of thespring mechanism, typically a beam structure, as it actually existswithin an operative oscillator, and is often distinct from the designwidth specified for the oscillator. The actual width, W_(real), of aspring mechanism is a function of the beam's design width (“W_(design)”)more or less some undercut value (“uc”) attributable to a fabricationprocess used to form the spring mechanism from a constituent materiallayer.

The term “fabrication process” describes a single fabrication step or asequence of steps that may be used to form a spring mechanism or masselement from a constituent material. Those of ordinary skill in the artwill recognize many conventional fabrication steps or sequence of stepsthat may be used to form a spring mechanism or mass element from a widechoice of conventional, constituent materials. Further, the term“constituent material” is not limited to only homogenous materials, butdescribes any single material or combination of materials susceptible toa fabrication process, such that a spring mechanism or mass element maybe formed.

The term “undercut” generally describes the physical response of aconstituent material to a fabrication process. Conventional etchingprocesses are ready examples of a fabrication process forming anoscillator element from a constituent material layer. Anisotropic,fluorine-based, plasma etching, such as that described in U.S. Pat. No.6,303,512 to Laermer et al. may be used to good effect within thecontext of the present invention. More specifically, the term “undercut”describes the accuracy with which a selected fabrication process may beapplied to the constituent material. Any lack of accuracy or “error”induced by a fabrication process may be attributable to, for example,variances in a photolithography step, non-vertical wall etching, etc.

The “total undercut value (uc),” is actually the sum of two factorsincluding; a “nominal undercut value (un),” and a “tolerance of undercutvalue (tu).” Undercuts may be positive or negative. A positive undercutwill remove more constituent material during a fabrication process thanis intended by design. Positive undercut “errors” thus result innarrower resonator components. A negative undercut will remove lessconstituent material than intended by the design, and result in widerresonator components. Typical total undercut values are positive andgenerally range from 0.1 μm to 1 μm. The foregoing relationship may bestated as follows:W _(real) =W _(design) −uc=W _(design)−(un+/−tu)  Equation 2

Nominal undercut values are well defined and understood for mostfabrication processes and their corresponding range of fabricationconditions (e.g., temperature, pressure, time, gas flaw rate(s), etc.).As a result, the nominal “error” induced during the fabrication of aspring mechanism or mass element by a selected fabrication process maybe specified to some degree of accuracy by the nominal undercut value.Accordingly, the nominal undercut value may be taken into account duringdesign of a spring mechanism and/or mass element.

For example, looking at FIG. 1C, the design width, W_(design), for abeam structure is typically specified to obtain a desired, actual widthW_(real) by adding (or possibly subtracting) the anticipated widthmargin associated with a nominal under cut value. In other words, thenominal undercut associated with a fabrication process may bepre-compensated or “sized into” the design.

Unfortunately, the same cannot be said for the variable tolerance ofundercut value. The error occurring in the fabrication of a springmechanism due to such process-tolerance-induced variations can not becompensated for during design. Until the present invention, thisprocess-tolerance-induced fabrication error seriously impacts theaccuracy with which MEMS resonators may be manufactured.

For example, conventional best practices have repeatedly been used toform a clamp-clamp beam structure designed to have an intended width of4 μm, and an intended length 100 μm. However, these repeated attempts toconsistently form an oscillator circuit having a spring mechanism widthdefining a 3.0 MHz frequency of interest have resulted in oscillatorsactually yielding output frequencies ranging from about 2.73 MHz to 3.24MHz. This represents a total range of frequency error exceeding 17%.Such frequency variations are unacceptable and such contemporary springmechanisms require extensive trimming to meet design specifications.

The present invention recognizes the important role played by theuncompensated tolerance of undercut associated with conventionalfabrication processes. By designing and fabricating a spring mechanismin accordance with the present invention, resonators having much greateraccuracy, approaching two or more orders of magnitude better thanconventional resonators, may be produced without extensive trimming.Thus, in one aspect, the present invention recognizes that themechanical stiffness of conventional spring mechanisms is oftenfundamentally impaired by undesired, process-tolerance-induced,variations in the width of the constituent beam(s) forming the springmechanism. If a beam's width is too narrow in relation to its design,its mechanical stiffness will be too low. If too thick, its mechanicalstiffness will be too high.

The present invention compensates for variations in spring mechanismstiffness as the result of process-tolerance-induced errors by alteringthe effective mass of a corresponding mass element in a discreteoscillator in a proportional, offsetting manner. Returning to FIG. 1A,as an illustrative example, the mechanical stiffness k_(y) of a springmechanism in the Y (lateral) direction is proportional to its effectivewidth, W_(real). This relationship may be expressed as: $\begin{matrix}{{k_{y} = \frac{E*h*W_{real}^{3}}{4*l^{3}}},} & {{Equation}\quad 3}\end{matrix}$where E is Young's Modulo, h is the beam height, and l is the beamlength.

Substituting the expression in Equation 2 for W_(real) above yields:$\begin{matrix}{k_{y} = {\frac{E*h*( {W_{design} - {uc}} )^{3}}{4*l^{3}}.}} & {{Equation}\quad 4}\end{matrix}$

The effective mass (m) of an assumedly rectangular beam structureforming the spring mechanism may be defined as:m=V*r=(A*h*r)=(l*W _(real) *h*r)  Equation 5,where V is volume, r is density of the constituent material, A is thesurface area of the upper face, and h is again the height of the beam.

Recalling equation 1, the resonance frequency (f) of this beam structuremay be expressed as: $\begin{matrix}{f = {\frac{1}{2 \cdot \pi} \cdot {\sqrt{\frac{k_{y}}{m}}.}}} & {{Equation}\quad 5}\end{matrix}$

Thus, in order to obtain a desired resonance frequency that isindependent of process-tolerance-induced variations, the ratio k_(y)/mmust be kept constant.

Continuing with the working assumption of a spring mechanism fabricatedfrom a rectangular beam structure and formed using conventional planaror surface micro-machining technologies, any process-tolerance-inducedvariance in the width of the spring mechanism will occur as an undercuterror through the surface area A of the upper face of the beam. Sincethe process-tolerance-induced undercut error is applied uniformly inFIG. 1A through the upper surface of spring mechanism 1 and the uppersurface of mass element 2, a proper definition of surface area A_(m) forthe mass 2 can be used to effectively compensate for theprocess-tolerance-induced undercut errors.

Stated in other terms, the present invention identifies a solution tothe problem of resonance frequency variations in discrete oscillatorscaused by variations in the mechanical stiffness of a spring mechanismas caused by process-tolerance-induced undercut errors. This solutionproperly defines the surface area of a corresponding mass in such a waythat the same process-tolerance-induced undercut error removes acorresponding, and therefore compensating, portion of mass m. Effectivemass is changed proportional to variations in actual width of the springmechanism. As a result, referring again to equation 5, effective mass(m) changes in proportional accordance with variations in the mechanicalstiffness (k_(y)) of the beam structure under the influence of afabrication process, such that the ratio k_(y)/m remains constant.

The concept of “proportionality” needs some emphasis at this point. Ascan be seen from equations 1 and 4 above, within the context of theworking example, a process-tolerance-induced undercut will affect thewidth of a spring mechanism and hence its mechanical stiffness k_(y), ina cubic manner while simultaneously affecting the effective mass in onlythe first order. (This relationship further assumes that mass element 2and spring mechanism 1 are formed from the same constituent material).Other proportionality relationships will exist for other geometries, andbeam-mass combinations of differing constituent material compositions.However, regardless of specific geometry and/or composition, the presentinvention provides, at least in one aspect, for maintenance of thefollowing relationship: $\begin{matrix}{{\frac{\partial\quad}{\partial{uc}}( \frac{k_{y}}{m} )} = 0.} & {{Equation}\quad 6}\end{matrix}$

The lack of an exact proportionality constant between mechanicalstiffness and actual mass, as well as normally occurring, yetunaccounted for variations in implementation of the fabrication processwill typically preclude maintenance of the foregoing ratio at exactlyzero. Thus, hereafter, the term “little change” will be used to describebest reasonable efforts to maintain at near zero the ratio between thechange in mechanical stiffness of the spring mechanism and the change inthe actual mass of the mass element. In a practical context,incorporation of the teachings of the present invention into the designand fabrication of a discrete oscillator has been experimentally shownto reduce the oscillator's frequency error by one to two orders ofmagnitude, within the tolerance of undercut (+/−tu), as compared withconventional oscillators of similar design.

There are numerous ways to implement a scheme wherebyprocess-tolerance-induced variations in the mechanical stiffness of aspring mechanism are compensated by proportional changes in acorresponding effective mass. Extending the example discussed inrelation to FIG. 1A, a proposed discrete oscillator 10 is shown in FIG.2. Here, spring mechanism 11 having effective width W_(real) isconnected between anchor 3 and mass element 13. Unlike the solid,conventional mass shown in FIG. 1A, mass element 13 is formed from aplurality of beam structures 15 preferably formed from the same materialas spring mechanism 11, and, preferably, having widths W_(mass), whereW_(mass) is ⅓ as wide as W_(real). This plurality of stacked and/orinterconnected beams 15 creates a mass element geometry that hasrelatively greater exposure to the effects of fabrication processundercut. Accordingly, relatively more mass is lost to the effects of apositive undercut. Any process-tolerance-induced undercut errorassociated with the fabrication process is applied equally to the widthof spring mechanism 11 and the respective widths of the plurality ofbeams 15 forming mass element 13. Accordingly, the tolerance of undercutassociated with the fabrication process will tend to move (increase ordecrease) both the mechanical stiffness of spring mechanism 11 and theeffective mass of mass element 13 in a similar manner. Where thegeometry of mass element 13 is appropriately selected in proportion tothe width of spring mechanism 11, little change results in the ratio ofchange in mechanical stiffness to the change in effective mass.

In the example of FIG. 2, the area of the mass element 13 can beexpressed as:A=N*W _(real) *l=N*(W _(design) −uc)*l  Equation 7,where N is the number and l is the length of the plurality of uniformlyformed beams 15. The effect of the fabrication process (i.e., theinduced change) on the effective mass of mass element 13 may becalculated in relation to the area A, and in relation to the rate ofreaction between the fabrication process and constituent materialforming the plurality of beams 15.

Other exemplary adaptations to the design and implementation of a masselement within a discrete oscillator system are shown in FIGS. 3A and3B. In a first general concept shown in FIG. 3A, the geometry of masselement 18, as it is exposed to a planar (surface micro-machining)fabrication process, is modified up or down by the inclusion or removalof voids 16 within the body of mass element 18. The inclusion ofadditional voids 16 within body of mass element 18 increases the numberof vertical edges acted upon by a typical planar fabrication process,and accordingly by an undercut associated with the fabrication process.Voids are included or removed as necessary to adjust the proportionalreaction of mass element 18 to a selected fabrication process used toform the actual width of a corresponding beam structure (not shown inFIG. 3A).

In a second general concept shown in FIG. 3B, the geometry of masselement 19 is modified to include an outer edge having a plurality ofindentations. The plurality of indentations has the effect of increasingthe vertical edge length of mass element 19 exposed to the planarfabrication process, and accordingly an undercut associated with thefabrication process, used to form beam width, W_(real). The term“indentations” as used hereafter denotes any discontinuous alteration inthe outer edge of a mass element that has the effect of increasing overa straight outer edge geometry the quantity of outer edge exposed to aplaner fabrication process. Thus, the term “indentation” includesorthogonal indentations, angular indentations, serrations, undulations,and similar geometries.

Either or both of the these techniques may be used in simulations, or inaccordance with a mathematical calculation to define an expanded surfacearea for a mass element that is susceptible to the fabrication processforming beam width W_(real) in such a manner that little change occursin the ratio of change in mechanical beam stiffness and the change inactual mass.

The foregoing examples have been given in relation to conventionalplanar (or surface micro-machining) processes typically used to formlateral beam structures. Wet etches, dry etches, plasma etches, andvapor etches are all amenable to the principles of the presentinvention. Furthermore, the present invention may readily be used tocompensate for process-tolerance-induced variations in out-of-planeoscillators, provided the geometric proportionality between changes inthe critical parameter defining resonance frequency and changes in acorresponding effective mass can adequately be defined or determined inrelation to one or more fabrication processes.

The foregoing examples all ascribe the change in effective mass to asingle fabrication process being simultaneously used to define theactual width of a beam structure. The practicalities of thisrelationship are readily manifest and it is presently preferred todefine mass element geometry in relation to the same fabrication processforming a corresponding beam structure width. Trimming of the masselement or beam is yet possible and can be conventionally performed, asnecessary. However, recent experiments have shown that trimming is notnecessary where mass element geometries are properly selected accordingto the dictates of the present invention. Indeed, resulting frequencyerrors of less than 0.15% (typical) have been achieved for oscillatordesigns previously exhibiting frequency errors greater/in the order ofthan 15%.

The examples thus far have all been drawn to discrete oscillatorsystems. Yet, the present invention is also applicable to continuousoscillator systems, such as those formed by the clamp-clamp beamstructure shown in FIG. 1B.

Numerous alterations to the conventional clamp-clamp beam structure arecontemplated within the context of the present invention. Severalexamples are shown in FIGS. 4A, 4B, and 4C.

In the example shown in FIG. 4A, voids 16 are formed in the length ofspring mechanism 20 with a similar intent as that ascribed to the voidsshown in FIG. 3A. Again, rectangular beam structures formed byconventional planar (or surface micro-machining) processes are assumedfor purposes of this explanation, but the present invention is not solimited. The vertical edges formed in the length of spring mechanism 20by voids 16 are necessarily affected by a planar fabrication processforming the actual width W_(real) of beam 20 By careful inclusion ofvoids within the beam design, the mass of continuous spring mechanism 20may be changed in proportion to the same process-tolerance-inducedundercut error defining the actual width of the beam structure.Accordingly, any variance in the mechanical stiffness of the springmechanism attributable to the fabrication process tolerances will becompensated for by proportional changes in the actual mass of the beam.

In the example shown in FIG. 4B, the outer edge of spring mechanism 20is designed to include indentations 17 of sufficient number and form tomaintain “little change” in the ratio of change in mechanical stiffness,as defined by the actual width of the beam W_(real), to the change inactual mass of the beam under the influence of the fabrication processused to form the actual beam width.

The example shown in FIG. 4C may be considered a hybrid designincorporating both discrete and continuous features. In this example,the geometry of spring mechanism 20 is more significantly altered toaccomplish the dictates of the present invention. Here, one or moreadditional mass structures 21 are formed integral to spring mechanism20. Additional mass structures 21 contribute to the overall mass ofspring mechanism 20, and further define the effective mechanicalstiffness of the whole structure. Consistent with the present invention,additional mass structures 21 make their contribution to the overallmass of spring mechanism 20 with an increased quantity of vertical edgearea exposed to the fabrication process, as compared with the continuousspring mechanism geometries previously described. When exposed to theplanar fabrication process forming beam 20, a properly defined geometryhas the effect of maintaining little change in the ratio of change inthe actual width of the beam to change in effective mass of the beam.Additional mass structures may include outer edge indentations and/orvoids to properly adjust the geometry being exposed to the fabricationprocess, and the undercut associated with the fabrication process.

Of further note in relation to the example shown in FIG. 4C, eachadditional mass structure 21 is anchored to spring mechanism 20 at oneor more anchor points 22. The exact location of such anchor points 22further defines the resonance frequency of the whole structure. Systemdesigners may adjust the additional mass structure anchor points tofurther refine the resonance frequency of their design.

The examples described thus far assume that the oscillator elements areall formed from the same constituent material. While this is preferred,it need not always be the case. For example, different constituentmaterials having similar, yet not identical, responses to a fabricationprocess might be used to form one or elements (or element portions) inan resonator structure. So long as the respectiveprocess-tolerance-induced undercut errors are proportionally controlledas between a resonance frequency defining parameter and a correspondingmass, the present invention finds application.

Taking yet another example, a mass element, like one described inrelation to FIGS. 2, 3A, and 3B, might be formed from a secondconstituent material type having a much higher relative etch rate tothat of a first constituent material type used to form a correspondingspring mechanism. Thus, in addition (or in alternative) to the designgeometry of the mass element, the selection of its constituent materialmight be used to maintain little change in the ratio of change in theresonance frequency defining parameter to the actual mass of acorresponding mass element. This is true for hybrid and continuousdesigns as well as discrete designs.

The foregoing examples describe lateral (Y-direction) oscillators. Forsuch systems, the height of the spring mechanism and/or the height ofthe mass element do not strongly influence the resonance frequency.However, out-of-plane oscillators may well need to consider the effectof component height on resonance frequency definition.

The present invention may readily be applied to many types ofoscillators including those with a variety of sense mechanisms, such ascapacitive, piezo-resistive, piezo-electric, etc. Further, a number ofdifferent actuation sources are contemplated for oscillators susceptibleto the present invention, including electrical, inductive,electrostatic, magnetic, thermal, piezo-electric, etc.

Single crystalline and or poly-silicon is a presently preferredconstituent material, but many other materials might be used with goodeffect.

In addition to the foregoing, the present invention further contemplatesthe incorporation of temperature compensation to maintain a desiredresonance frequency over a prescribed range of operating temperatures.U.S. patent application Ser. No. 10/414,793 filed Apr. 16, 2003 (asAttorney Docket 207.003-US) describes various methods and techniques bywhich the resonance frequency of a MEMS oscillator may be maintainedover temperature. This co-pending, commonly assigned application ishereby incorporated in its entirety by reference.

1-26. (canceled).
 27. A resonator comprising: a spring-mass mechanism,having an effective mechanical stiffness and an effective mechanicalmass defined by a geometry; wherein the geometry and the effective massof the spring-mass mechanism are simultaneously defined by applicationof a fabrication process to a constituent material; and wherein thegeometry is defined such that application of the fabrication process tothe constituent material results in little change to a ratio defined bya change in the effective mechanical stiffness and a change in theeffective mechanical mass.
 28. The resonator of claim 27 wherein thegeometry of the spring-mass mechanism comprises one or more voids formedin the length of the spring-mass mechanism.
 29. The resonator of claim27 wherein the geometry of the spring-mass mechanism comprises an outeredge having a plurality of indentations, the plurality of indentationshaving the effect of increasing a surface area of the outer edge exposedto the fabrication process.
 30. The resonator of claim 27 wherein thespring-mass mechanism includes at least one mass structure that isformed integral to the spring-mass mechanism.
 31. The resonator of claim30 wherein at least one of the mass structure comprises one or morevoids formed in a body of the at least one mass structure.
 32. Theresonator of claim 30 wherein at least one of the mass structurecomprises an outer edge having a plurality of indentations, theplurality of indentations having the effect of increasing a surface areaof the outer edge exposed to the fabrication process.
 33. The resonatorof claim 32 wherein the at least one of the mass structure furthercomprises one or more voids formed respectively in a body of the atleast one of the mass structure.
 34. The resonator of claim 27 whereinthe spring-mass mechanism includes a plurality of mass structures thatare formed integral to the spring-mass mechanism.
 35. The resonator ofclaim 34 wherein each of the plurality of mass structures includes oneor more voids formed in a body of the mass structure.
 36. The resonatorof claim 34 wherein each of the plurality of mass structures includes anouter edge having a plurality of indentations, wherein the plurality ofindentations having the effect of increasing a surface area of the outeredge exposed to the fabrication process.
 37. The resonator of claim 36wherein each of the plurality of mass structures further includes one ormore voids formed in a body of the mass structure.
 38. The resonator ofclaim 27 wherein the spring-mass mechanism includes a plurality ofspring structures that are formed integral to the spring-mass mechanism.39. The resonator of claim 38 wherein each of the plurality of springstructures includes one or more voids formed in a body of the springstructure.
 40. The resonator of claim 38 wherein each of the pluralityof spring structures includes an outer edge having a plurality ofindentations, and wherein the plurality of indentations having theeffect of increasing a surface area of the outer edge exposed to thefabrication process.